Fuel pump



Ap 948- K. J. DE JUHASZ ET AL 2.440.194

FUEL PUMP Filed Jan. .29, 1946 5 Sheets-Sheet 1 IN ENTORS KALMANJ- z w-msz A'ITOR Y P 20, 1948- K. J. DE JUHASZ ET AL I 2,440,194

FUEL PUMP Filed Jan. 29, 1946 5 Sheets-Sh eet 2 |Nv N ToRs KALMANJDE UHASZ April 20, 1948.

k. J. DE JUHASZ r AL 2.440.194

FUEL PUMP Filed Jan. 29, 1946 5 Sheets-Sheet 3 INV NTORS KALMANJDE (/HASZ FHA'DEP/c/r :1 VII. 1. FaRTAgJ/R BY HI ATT E April 1948- K. J. DE JuHAsz mm. 2,4

FUEL PUMP Filed Jan. 29, 1946 5 Sheets-Sheet 4 mv TORS KALMA/v-J. E UHASZ iatented Apr. 20, 1948 Frederick J.

Villi'orth, Jr.,

Beacon, N. Y., as-

.signors to The Texas Company, New York, 'N. Y., a corporation of Delaware Application January 29, 1948, Serial No. 644,032

20 Claims.

This invention relates to a fuel pump and timer mechanism for an internal combustion engine operating with fuel injection.

A principal object of the invention is to provide a, novel fuel pump of this character capable of drawing fuel from a lower pressure source and supplying it to the injection line of the engine at a constant high injection pressure during the injection period on each cycle, and then reducing the fuel pressure in said injection line immediately at the termination of the injection period to avoid dribbling from the nozzle.

A further object is to provide a fuel pump and timer mechanism of the above character which also permits accurate control and adjustment of the injection advance and duration of injection during each cycle, even in the engines.

Still another object of the invention is to-provide a fuel pump and timer assembly which is compact and rugged and construction, reliable in operation, readily and simply adjusted to vary the injection advance and duration of injection, and capable of rapid or snap-action movement in initiating and terminating injection on each cycle, while at the same time accurately maintaining the fuel pressure control and the injection timing over long periods of service.

Other objects and advantages of the invention will be apparent from the following description when taken in conjunction with the appended claims and the attached drawing.

A preferred embodiment of the invention is illustrated in the drawing, wherein Fig. 1 is a side elevational view of the pump and timer assembly with high pressure fuel reservoir connected thereto;

Fig. 2 is a top plan view of assembly;

Fig. 3 is a vertical sectional view taken on the plane of the line 3-3 of .Fig. 2;

Fig. 4 is a vertical sectional view taken on the plane of the line 4-4 of Fig. 2;

Fig. 5 is a partial, vertical, sectional view on an enlarged scale of one of the pumping cylinders, with the associated pump plunger shown in elevation, the view being taken at right angles to that of Fig. 3; and

Fig. 6 is a view similar the plane of Fig. 3 and Fig. 5.

As illustrated in the drawing, fuel is supplied from a lower pressure source of supply through pipe 2| to the pump and timer assembly indicated generally by the numeral 22. The latter the pump and timer to Fig. 5, but taken in at right angles to that of serves to supply fuel under a constant high pressure during the injection period on each cycle case of high speed v through injection line 23, which is adapted to lead to the conventional injection nozzle for injecting fuel into the combustion space of the engine cylinder. The pump and timer assembly 22 controls the beginning and end of injection, as well as maintaining a constant high injection pressure in the fuel injection line 23 during the injection period; and also serves to release the pressure in fuel line 23 immediately at the end of the injection period, whereby the customary pintle valve in the injection nozzle of the engine is adapted to slam shut on its seat to prevent dribbling of fuel from the nozzle tip.

The pump and timer assembly 22 comprises a crank-case 80 and a cylinder block 8I which are bolted together by bolts 82. Crankcase 80 is provided with opposed cover plates 83 and 84 providing access to the interior of the oil reservoir 85. Plate 84 is provided with a drain plug 86. A screw plug 05 closes the upper end of a passage (not shown) drilled through blocks and and 8| which enables the reservoir to be supplied with lubricating oil. Crankcase 80 is also provided with end cover plates 8'! and 88 containing oil seals 89 for a camshaft 90 which is adapted to be interconnected with the engine in any suitable manner to'be driven at camshaft speed, which is one-half the engine speed for four-cycle operation. Camshaft 90 is mounted on ball bearings SI, and carries within oil reservoir 85 three cams indicated by the numerals 92, 9a and 94 respectively. Cams 92 and 94 are identical incontour, and are displaced 90 angular degrees apart for a purpose hereinafter described.

Cylinder block BI is provided with a threaded opening receiving a pipe pressure fitting 91 to which is connected line 2| leading to the low pressure fuel supply. The cylinder block 8| is drilled to form a channel 98 (Fig. 2) communicating with branch bores98 and I00 respectively, which latter supply pumping units IOI and I02 respectively. These pumping units operate in parallel to supply fuel from the low .pressure source to,a storage reservoir I03 (Fig. 1) maintained under the desired constant high fuel pressure employed for fuel injection.

The pumping units are of identical construction, and unit I 0| is illustrated in cross-section in Fig. 3 and in elevation in Fig. 4. Enlarged detailed views of a portion thereof are shown in Figs. 5 and 6. This pumping unit comprises a pump cylinder I04, within which operates a plunger I05. Cylinder I04 is provided with an inlet port I08 communicating with bore 88. through which fuel is fed into the interior of the pump cylinder on the down or suction stroke of the plunger I05. Somewhat below the elevation of inlet port I08, cylinder I04 is formed with a spill port I08 communicating with cross channel I08 formed in the cylinder block 8|, the cross channel I08 also extending to the corresponding spill port of pump unit I02 (Fig, 2). Leadingoif from the cross channel I08 is a passageway IIO which communicates with pipe fitting III, to which is fastened fuel line II2 leading back to the source of low pressure fuel supply. 1

Plunger I is formed with an interior axial bore II2 leading from the upper end to radial ports II3 communicating with an annular channel 4 formed by a circular groove about the plunger. The latter is shown in Figs. 3 and 6 immediately below the level of the spill port I08, the plunger being shown in its upper dead center position in this view. The plunger is also formed with an inclined groove providing a helix II5 extending slightly more than 90 about the circumference thereof from an upper vertical groove I I8 down to the annular channel I I4, and adapted to cooperate with the spill port I08 to control the amount of fuel supplied to the high pressure reservoir I03 on each working stroke,

Carried by the upper end of cylinder I04 is a check valve housing II1 carrying a check valve H8 having a depending stem slidingly disposed within the check valve body and drilled to form a vertical channel II8 communicating with the pump cylinder above the plunger. the upper end of the vertical channel 8' being i turn connected by radial ports with an annular fuel chamber II9. 0n the working stroke of plunger I05, fuel under high pump pressure is forced into the annular chamber II8 where it acts on the inclined surface of the check valve and raises it from its seat against the action of spring I20. The lower end of the spring is mounted about a central extension of check valve 8, the spring bearing on the upper face of the check valve. Surrounding the upper portion of check valve H8 and the lower portion of spring I20 and spaced therefrom is a fuel passage collar I22 provided with radial ports I22 opening into an annular channel communicating with the high pressure cross bore I23 formed in cylinder blockIiI. This cross bore I23 is above and in approximate alignment with the cross bore I09, as shown in Fig. 2, and provides communication of both pumping units with the high pressure discharge channel I24 opening into a vertical channel I25. The upper end of channel I25 communicates with pipe fitting I26 to which is connected line I21 leading to high pressure storage reservoir I03 (Fig. 1). The upper end of the pumping unit is closed b a fitting I28 having a sealing block I30 held in place by sleeve nut I3 I.

The lower end of pump cylinder I04 receives a sleeve I33 which is free to rotate about the cylinder, The upper end of sleeve I33 carries a spur gear I34 meshing with rack I35 which is slidably mounted for horizontal longitudinal movement within a bore formed in cylinder block 8|. A cap screw carries an extension riding in a slot in rack I35, thus maintaining the parts in proper alignment. The lower end of plunger I05 has rigidly fastened thereto a sleeve I31 provided with a lug I38 extending through a slot in the depending portion of sleeve I33, so that rotation of sleeve I33 causes corresponding rotative movement of plunger I05 I36 threaded in the block 8| within the cylinder I04. This changes the position of helix I I5 with respect to the spill port I00, and consequently varies the quantity of fuel supplied to the high pressure sourceon each working stroke. Thelower end of plunger I05 carries a spring retainer I40 receiving spring I, the upper end of which bears against a shoulder carried by sleeve III. A cam follower I42 is slidably mounted within a suitable bore in the crankcase 80, and is cup-shaped to receive the lower end of the plunger. the spring I and related parts. Spring I4l forces the cam follower to ride on the cam 84 with the desired pressure.

As shown in Fig. 3, cam 84 (as well as com 82 which is of identical shape) is formed with two lobes to provide two working strokes for each rotation of the cam-shaft. As shown in Figs. 3 and 4, cams 82 and 84 are arranged apart, so that the pumping strokes of units IN and I02 occur alternately. Each of the pumping units is automatically controlled through rack I35 to maintain a predetermined high fuel pressure within the reservoir I03. This is accomplished in the following manner:

The vertical channel I25 communicates at its lower end with a passage I45 constituting a plunger pressure chamber. Mounted within said passage I45 is a plunger cylinder I48 slidably receiving a plunger I41. At the outer end of passage I45, there is threaded into block 8| and extension I48 of a pressure control cylinder I50. Extension I48 has an interior machined bore within which is slidably mounted a second plunger or sliding rod I5I. Plunger I41 is provided with a bearing cap at the left hand end thereof (Fig. 4) which engages the rounded end portion of plunger I5I. It will be understood that the fuel pressure within reservoir I03 is communicated through pipe I21 and passage I25 to pressure chamber I45, and acts on the exposed end of plunger I41, tending to force the plungers I41 and I5I to the left as shown in Fig. 4.

Pressure control cylinder I50 is provided with a cover plate I53 having a threaded opening I54 adapted to receive a pipe connection leading to a source of fluid under constant pressure. For example, air supplied by a suitable compressor, is forced through a pressure regulating valve (not shown) into a suitable air reservoir, where it is maintained at the desired constant pressure; and this air then passes through a check valve in the pipe connection fastened to opening I54 and thence intov the interior of pressure regulating cylinder I50 where it acts on piston I55. The latter is slidably mounted within cylinder I50 so that the air pressure tends to move the piston to the right as shown in Fig. 4, Piston I55 is provided with spaced lugs I51 and I58, the ends of which bear against the head of plunger I5I. Consequently, the air pressure within cylinder I50 on the left hand or interior side of piston I55 acts against and is normally substantially balanced by the fuel pressure in chamber I45 acting against the face of plunger I41. It will be understood that a very high fuel pressure acting on the comparatively small area of the exposed face of plunger I41 can be balanced by a relatively low and conveniently supplied air pressure acting on the much greater cross-sectional area of piston I55.

Instead of the construction shown including the source of constant air or other fluid pressure, piston I55 and cylinder I50, it will be understood that a suitable spring with adjustable compression can be employed to counteract the thrust of the fuel pressure on the plunger. However, where an air compressor or other convenient source of low pressure fluid is available, the construction shown is preferred, since it is readily maintained in accurate operating condition over long periods of time, and is not subject to wear and variation in compression for a given setting as is the case with a spring.

Loosely pinned between lugs I51 and I58 by pin I80 is a lever I8I. The latter, as shown in Fig.2, extends through suitable slots in the opposite sides of cylinder I50 beyond the normal range of travel of piston I55. Some air leakage between piston I55 and cylinder I50 may occur, this leakage escaping to atmosphere through the said slots. This is unobjectionable since a reservoir of sumcient capacity can be provided to maintain the air pressure within cylinder I50 substantially constant for any given position of piston I55. Necessary makeup air for this purpose is supplied to the reservoir through the mentioned pressure regulating valve from the compressor or other source of supply. One end of lever'I8I is pivoted at I83 to a stud or post I84 extending outwardly from block 8I. The other end of lever I M is pivoted at I85 to a short link I68, which in turn is pivoted at I 81 to the end of rack I35. As shown in Fig. 4, pin I80 rides loosely within a longitudinal slot formed in lever I6I to permit swinging movement of said lever about its pivot I83 upon longitudinal movement of piston I55 within cylinder I50.

It will thus be seen that, if the pumping units IOI and I02 are operating to supply fuel to reservoir I03 at a rate faster than fuel is supplied by line 23 to the engine, which causes an increase in fuel pressure in reservoir I03 and also in pressure chamber I45, this will causemovement of piston I55 to the left (Fig. 4). Since the abovementioned check valve in the air supply line to cylinder I50 opens one way only to permit flow of air to cylinder I50 but prevents reverse flow of air, the air pressure within cylinder I50 will increase upon this movement of piston I55 and eventually balance the increased fuel pressure in chamber I45. Movement of the piston I55 to the left swings lever I8I about pivot I83, so that the opposite end of lever I6I pivoted at I65 swings in a counter-clockwise are as shown in Fig. 2. This movement through the interconnecting link I86 will slide rack I35, so that said rack moves upwardly as shown in Fig. 2 or away from the observer as shown in Fig. 3. This movement of rack I35 rotates the spur gears I34 of the pumping units IOI and I02 in a counterclockwise direction (Fig. 2), thereby bringing a higher portion of each helix I I5 of the plungers I05 opposite the respective spill ports I08. Consequently, on the up or working stroke of each plunger I05, the inclined groove formed in the plunger will be brought into registration with spill port I08 at an earlier period in the cycle. At this moment, fuel trapped under the high supply pressure above plunger I05 is permitted to escape through the axial bore H2, radial ports II3, annular groove H4 and inclined groove to the spill port I08, and thence return by passage I08, channel II and line I I2 to the low pressure fuel supply. The net result is a decrease in the amount of fuel supplied to reservoir I03 by the pumping units on each working stroke, resulting in a drop in pressure in fuel chamber I45 and reservoir I03. The excess air pressure behind the piston I55 in cylinder I50 then moves piston I 55 and the associated plungers II and I41 to the right (Fig. 4)

6 to restore the parts to normal position and mainllziian the predetermined fuel pressure in reservoir Conversely, if the pumping units IM and I02 are supplying insufllcient fuel to satisfy'the ensine demand, the pressure in reservoir I03 and fuel chamber I45 drops, and the air pressure within cylinder I 50 then moves piston I55 to the right. This causes a reverse movement of lever IBI and rack I35 from that previously described, and rotates a clockwise direction (Fig. 2), thereby bringing a lower portion of each helix I I5 opposite its respective spill port I08. The pumping units I01 and I02 then supply an increased quantity of fuel on each working stroke to-maintain the fuel pressure-within reservoir I03 substantially constant. It will be understood that the size of reservoir I02 as shown in Fig. 1 is substantially smaller than is actually employed, this being done as a matter of convenience in illustration. Actually, the reservoir I03 may be several times the size of the pump and timer assembly 22 as shown in this figure. It will be seen that the pumping units IOI and I02 and the fluid pressure control cylinder I 50 serve to automatically maintain a supply of fuel in reservoir I03 under a substantially constant high injection pressure during the operation of the engine. However, these units do not control the beginning and duration of fuel injection. The latter is accomplished by the timer mechanism of assembly 22 which will now be described.

Referring to Fig. 1, reservoir I03 is connected by fuel feed line I10 to pipe connection I1I (Fig. 2) mounted on the side of block M. This in turn communicates with fuel channel I12 (Figs. 2 and 3) opening into an annular chamber I13 (Fig. 3) formed in the fuel passage collar I14 of the timer mechanism indicated generally at I15. This mechanism is shown in cross-section in Fig. 3. A cylinder I11 rigidly carried by block 8| receives a plunger I18. The latter is provided with a circular groove forming a portion of smaller exterior diameter I18. This provides a fuel chamber adapted to communicate with the upwardly inclined passages I drilled through cylinder I 11 and which open into a spill port I8I formed in block 8|. As shown in Fig. 2, said spill port I8I comprises a short passage communicating with channel I I0, thus leadi the discharged fuel through pipe fitting I II and line I I2 back to the source of low pressure fuel supply.

Above spill port I8I, sleeve I11 is drilled to form radial ports I83 which communicate with a passage I84 in block 8| leading to pipe fitting I85. As shown in Fig. 1, fuel line 23 leading to the engine is connected to said fitting I85. Formed on sleeve I11 is a valve seat I81 for a check valve I88 normally held on its seat by spring I88. The valve seat I81 is within the lower portion of the fuel passage'collar I14, which latter bears against a packing ring surrounding the upper end of sleeve I11. A fitting I80 threaded in block 8| clamps a. second packing ringagainst the upper surface of collar I14 and maintains the parts in assembled relationship. The outer end of fitting I80 is sealed by plug I8I held in place by sleeve nut I82.

Fuel from chamber I13 passes through radial ports in collar I14 to the space above check valve I88. It will be noted that the check valve has an upwardly extending central portion which is surrounded by the lower end of spring I88, the latter bearing at its lower end against the top face the sleeves I 33 and plungers I05 in side of said radial ports I83 what from the lower end of the check valve stem.

of the check valve and at its upper end against the fltting I90. The check valve I88 is also provided with a downwardly extending stem carrying guiding fins, the lower end of said stem being shown in Rig. 3 as terminating opposite the radial ports I83. In this same view, the upper end of plunger I18 is shown as about even with the lower and spaced some- This upper end of plunger I18 is drilled to provide an axial channel communicating at its lower end with radial ports which are shown in registration with the ports I80 in sleeve I11 leading to spill port'I8I. Thus, as shown in Fig. 3, channel I84 and consequently the fuel supply line 23 (Fig. l) is open to the low pressure fuel supply through ports I83, the axial bore and radial ports formed in the top of plunger I18, ports I80, spill port I8I, channel I I0, and line II2. This means that the fuel pressure in line 23 has dropped to the low pressure of the main supply from line 2I, and consequently fuel injection has been terminated.

Initiation of the injection on the succeeding cycle is accomplished by upward movement of plunger I18 to contact the depending stem of check valve I88 to raise the latter from its seat I81. The construction is such that the depending stem of the check valve first seals the axial bore at the upper end of plunger I18, thereby preventing fuel flowing from ports I83 to the spill port IBI. Further upward movement of plunger I18 raises check valve I88 from its seat, and allows high pressure fuel from the space above the check valve, and consequently from reservoir I03, to flow downwardly through the fluted passageway about the depending check valve stem to ports I83 and thence by channel I84 to fuel line 23. This immediately raises the presof which is shown in elevation in Fig. 3. Referring to Fig. 4, the spaced forks 208 are adapted to straddle cam 83 and to bear on the circular portions of cam shaft 80 on opposite sides of said cam 08. Also carried by said lever arm 201 and extending between said spaced forks 208 is a bearing pin 208 adapted to contact the rise of cam 93.

sure in fuel line 23 to the constant injection pressure to start fuel injection.

Termination of fuel injection on each cycle is accomplished by causing plunger I18 to move downwardly to seat check valve I88, and then withdrawing the top of the plunger from the depending check valve-stem, thereby opening communication between fuel line 23 and the spill .port I8I as previously described to immediately drop the pressure in the fuel line 23 to the lower pressure of the main fuel supply.

For high speed internal combustion engines, a very rapid or snap movement of the timer plunger I18 is required. This is accomplished by the mechanism now described. As shown in Fig. 3, the lower end of plunger I18 carries a spring retainer I85 which receives the lower portion of a spring I96, the upper portion of which bears against block 8|. Surrounding the lower portion of spring I96 is a, cup-shaped cam follower I81 slidably mounted within a machined bore in crank case 80. The underside of follower I91 carries a depending lug I98 held in engagement by spring l86 with a hardened steel bearing ball I98 mounted in the upper end of a bolt 200 threaded in the arm 20I of a bell crank lever. Bolt 200 is locked in adjusted position by lock nut 202. v

The said bell crank lever is rotatably mounted on eccentric journal 204, the latter protruding eccentricaily from a shaft 205 rotatably mounted in a sleeve bearing carried by crank case 80. Shaft 205 is indicated in dotted lines in Fig. 3, and the outer end of said shaft which protrudes to the exterior of the crank case 80 is shown in Figs. 1 and 2. The second arm 201 of said bell crank lever is formed with spaced forks 208, one

With the cam 88 in the position shown in Fig. 3, it will be seen that the forks 208 are then riding on the circular portion of cam shaft and timer plunger I18 is in its lower-most position. Therise of cam 83 is relatively steep. Consequently, as cam shaft '80 rotates, this rise is brought into contact with hearing pin 208, and due to the steepness of the rise, a very quick clockwise rocking movement of lever 20I-201 results, causing a fast upward movement of timer plunger I18 to initiate injection at the proper point in the cycle. Likewise, the slope of cam 83 on the descending side is also steep, producing a rapid lowering movement of timer plunger I18 to terminate fuel injection.

, The duration of fuel injection is varied by rotation of shaft 205 within its bearing in crank case 80, and this is under the control of the throttle. As shown in Figs. 1 and 2, a lever 2 is rigidly fastened to the outer exposed end of shaft 205. Pivotally connected at 2 I2 to the end of lever 2 is a. rod 2I3 which leads to the usual throttle control located at the operators compartment. Due to the eccentric mounting of pin 204 in shaft 205, rotation of shaft 205 will cause movement of the center of pin 204 toward-or away from cam shaft 80'on an arc indicated by the arrow in Fig. 3. As this occurs, depending sides of forks 208 slide along cam shaft 80 and continue to bear thereon, and bearing pin I98 slides along the broad bearing surface of depending lug I88 and also maintains engagement therewith. However, bearing pin 209 is at the same time moved either closer to or farther away from the center of cam shaft 90. Rotation of throttle lever 2 in a counter-clockwise direction (Fig. 1) will move bearing pin 208 farther away from the center of cam shaft 90. This means that the rise of cam 93 will contact pin 208 later in the cycle, and likewise, the descending side of cam 93 will leave pin 209 earlier in the cycle. Duration of fuel injection is thus shortened by starting injection later and terminating injection earlier in the cycle. Conversely, rotating throttle lever in a clockwise direction (Fig. 1) will move bearing pin 208 closer to the center of cam shaft 90, and thereby increase the duration of fuel injection by starting injection earlier and terminating injection later in the cycle.

From the above description, it is seen that the fuel pump and timer assembly 22 accomplishes several functions. It controls the beginning and end of fuel injection in each cycle, and enables the duration of fuel injection to be varied in accordance with the load on the engine. Further, it maintains a substantially constant high fuel pressure within the fuel line 23 during the period of fuel injection, which pressure is sufllciently high to initiateopening movement of a conven-- tional spring-pressed pintie valve in the fuel injection nozzle. Finally, it immediately drops the fuel pressure in line 23 to a lower value whichin the cycle at which injection starts and the time in the cycle at which injection terminates are both varied in accordance with the load on the engine, constitutes a preferred arrangement,

it will be understood that other arrangements can be employed. Thus, the time inthe cycle of initiating injection can be maintained substantially constant, and the duration of injection regulated by varying the time of terminating injection, or vice versa. 1

It will be understood that the relative location of the pivot pin 2 with respect to the cam shaft 80, as well as the eccentricity of pin 204 with respect to the center line of shaft 205, can be varied to suit the particular installation and the operating characteristics of injection advance and duration of injection desired. Likewise, the contour-of cam 93 can be varied and coordinated with the mounting of lever [-201 to alter these injection characteristics. Additional control and ease of adjustment is afforded by the bearing pin I98 carried by the adjustable bolt 200, which latter is readily accessible upon removal of cover plate 84. Thus, adjusting bearing pin l99 downwardly as shown in Fig. 3 serves to move the upper end of timer plunger I18 farther away from the lower end of the depending stem of check valve I88. Consequently, for any given setting of shaft 105, this will initiate injection later in the cycle and terminate injection earlier in the cycle, with a net reduction in the duration of injection on each cycle. The upper limit of adjustment of bearing pin I99 is determined by that setting which just removes the lower end of the check valve stem from sealing engagement within the upper end of the axial passage of the timer plunger MB. This position is maintained throughout the major portion of the cycle by the spaced form 208 riding on the circumference of the circular portion of the cam during the brief interval on each cycle when the single rise having steep sides of cam 93 contacts bearing pin 209 and rocks the lever with spaced forks 208 away from the surface of the circular cam shaft that the injection period occurs.

The fuel pump and timer assembly of the present invention is particularly adapted, for use in connection with an engine operating with nonmocking combustion, wherein combustion is initiated by spark ignition promptly after the start of injection to form a flame front, and injection is then continued into localized portions of the combustion space in advance of the flame front, as disclosed and claimed in the copending application of Everett M. Barber, Serial No. 513,232, filed December 7, 1943, now abandoned. Moreover, the present invention is particularly useful for an engine of this character equipped with a control to vary the rate of fuel injection in accordance with the fluid density within the combustion space during the injection period, as disclosed and claimed in the copending application of Everett M. Barber and Jay E. Malin, Serial No. 623,098, filed October 18, 1945.

Obviously many modifications and variations of the invention, as hereinbefore set forth, may be made without departing from the spirit and scope thereof, and therefore only suchlimitations should be imposed as are indicated in the appended shaft 90; and it is only claims.

We claim: 1. A fuel pump and timer assembly for an internal combustionengine operating with fuel injection and having a fuel injection line, comprising a pump block having a pump cylinder 1 10 and a plunger operating therein, an inlet from a source of low pressure fuel supply communicating with said pump cylinder, a high pressure fuel storage chamber, an outlet from said pump cylinder communicating with said storage chamber, said pump block also having a timer cylinder and a plunger operating therein, an inlet to said timer cylinder communicating with said storage chamber, .an outlet from said timer cylinder adapted to be connected to said fuel injection line of the engine, a spill port from said timer cylinder communicating with a return line to said low pressure fuel supply, a cam shaft mounted in said pump block, operative interconnections between said cam shaft and said pump and timer plungers, means for automatically controlling the operation of said pump plunger to regulate the supply of fuel from said low pressure source to said storage chamber to maintain a predetermined substantially constant high pressure of fuel within said storage chamber, and means associated with said timer plunger for controlling the beginning of injection on each cycle by connecting said timer cylinder inlet to said timer cylinder outlet while closing said spill port to thereby provide fuel flow from the storage chairber to the fuel injection line at the substantially constant high fuel pressure, and for regulating the end of injection on each cycle by connecting said spill port with said timer cylinder outlet while closing said timer cylinder inlet to thereby immediately reduce the fuel pressure in said fuel injection line to a substantially lower value,

2. A fuel pump and timer assembly according to claimv 1, wherein said operative interconnection between. said cam shaft and said pump plunger includes a cam directly engaging a cam follower attached to said. pump plunger, and the operative interconnection between said cam shaft and said timer plunger includes a second cam operating through apivoted lever on a cam follower of said timer plunger, said parts being constructed and arranged to providev a snapaction movement of said timer plunger.

3. A fuel pump and timer assembly according to claim 1, wherein the operative interconnection between said cam shaft and timer plunger includes a cam with a rise having steep sides, a lever having an arm provided with spaced forks adapted to ride on said cam shaft on opposite sides of said cam, a bearing pin carried between said spaced forks and adapted to be engaged by said cam rise to rock said lever with a snapaction movement, a cam follower carried by said timer plunger and having a broad bearing surface, an adjustable bearing tip carried by the other arm of said lever and engaging said broad bearing surface, an eccentric journal carried by a shaft mounted in said pump block and providing a pivot for said lever, and means for rotating said shaft to thereby move said eccentric journal in an arc to adjust the-position of said bearing pin with respect to said cam to alter the duration of injection on each cycle.

4. A fuel pump and timer assembly according to claim 1, wherein the means for automatically controlling the operation of said pump plunger comprises a spill port formed in said pump cylinchamber, a control piston'movable in response to changes in fuel pressure in said storage chamber, and operative interconnections between said plunger cooperating with said spill port, means for rotating said pump plunger to adjust the time in the pumping stroke of said plunger when said helix opens the said spill port to terminate the supply of fuel through said pump outlet to the said storage chamber, a pressure chamber formed in said pump block and communicating with said storage chamber to receive fuel under said high fuel pressure, a piston mechanism including a piston slidably mounted in said pump block and having an end of relatively small cross-sectional area exposed to the high pressure of fuel in said pressure chamber, means opposing movement of said piston in response to the force exerted by the high fuel pressure on the end of said piston and normally holding the piston in an equilibrium position at said predetermined constant fuel pressure, and operative interconnections between said piston mechanism and said means for rotating the pump plunger to regulate the angular position of said pump plunger in accordance with the position of said piston.

6. A fuel pump and timer assembly according to claim 1, wherein the means for automatically controlling the operation of said pump .plunger comprises a spill port formed in said pump cylinder and communicating with said return line to the low pressure fuel supply, a helix on said pump plunger cooperating with said spill port, means for rotating said pump plunger to adjust the time in the pumping stroke of said plunger when said helix opens the said spill port to terminate the supply of fuel through said pump outlet to the said storage chamber, a pressure chamber formed in said pump block and communicating with said storage chamber to receive fuel under said highfuel pressure, a piston slidably mounted in said pump block and having an end of relatively small cross-sectional area exposed to the high pressure of fuel in said pressure chamber, a fluid pressure cylinder, a second piston Of relatively large crosssectional area slidably mounted in said fluid pressure cylinder and operatively engaging the other end of said first-mentioned piston, means adapted to connect said fluid pressure cylinder with a source of fluid under a substantially constant pressure which is lower than said high fuel pressure, whereby the force of the lower fluid pressure on said second piston of relatively large cross-sectional area balances the force of said high fuel pressure on said first piston of relatively small cross-sectional area and holds the parts in equilibrium at said predetermined high fuel pressure, and operative interconnections between said pistons and said means for rotatin the pump plunger to regulate the angular position of said pump plunger in accordance with the positions of said pistons.

'7. A fuel pump and timer assembly according to claim 1, wherein the means associated with said timer plunger for controlling the beginning and end of injection comprises a check valve normally closing communication between said timer cylinder inlet and outlet, said timer plunger having an axial passage normally providing communication between said timer cylinder outlet and spill port, and a stem carried by said check valve adapted to seat within and seal said axial passage at the beginning of the injection stroke of said timer plunger to close communication between said timer cylinder outlet and spill port, and then to open said check valve on further movement of the timer plunger on its injection stroke to provide communication between said timer cylinder inlet and outlet.

8. A fuel pump and timer assembly according to claim 1, wherein the pump block is provided with two pump cylinders with pump plungers of similar construction connected in parallel to force fuel from said low pressure source to said high pressure fuel chamber, and the cam shaft is provided with two cams having rises of similar contour for operating said pump plungers, said cams being angularly displaced on said cam shaft so that said pump plungers operate alternately.

9. A fuel pump and timer assembly according to claim 1, wherein the pump block is provided with two spaced pump cylinders and pump plungers of similar construction mounted in alignment with said cam shaft and connected in parallel to force fuel from said low pressure source to said high pressure fuel chamber, the said timer cylinder with timer plunger being mounted in said pump block intermediate said two spaced pump cylinders and being offset from said cam shaft, the latter being provided with a cam having one rise with steep sides for the snap-action operation of said timer plunger once on each rotation of the cam shaft, and the latter also being provided with two additional cams of similar contour on opposite sides of said first-mentioned cam, each of the two additional cams having two rises with less steep sides, and with the two rises of one cam angularly displaced by 90 from the corresponding two rises of the other cam, whereby the pump plungers operate alternately with each having two working strokes on each rotation of the cam shaft.

10. A fuel pump and timer assembly for an internal combustion engine operating with fuel injection and having an injection line, comprising a pump block, a high pressure fuel chamber, a

pump cylinder with pump plunger mounted in said block and connected to force fuel from a low pressure source to said high pressure fuel chamber, a timer cylinder with timer plunger mounted in said pump block and connected to control the supply of fuel from said high pressure fuel chamber to said injection line, driving means in said pump block for reciprocating said pump plunger and said timer plunger, means associated with said timer plunger for regulating the beginning and duration of supply of fuel from said high pressure fuel chamber to said injection line on each cycle, said means being constructed and arranged to close communication between said fuel chamber and said injection line and maintain a substantially lower fuel pressure in said injection line during the balance of each cycle, and means associated with said pump plunger and responsive to fuel pressure within said high pressure fuel chamber for automatically regulating the supply of fuel from said low pressure source to said high pressure fuel chamber to maintain a predetermined substantially constant pressure of fuel. in the latter.

11. A fuel pump and timer assembly for an in- 13 ternal combustion engine operating with fuel in- Jection and having an injection line, comprising a pump block, a high pressure fuel chamber, two spaced pump cylinders having pump plungers mounted in said block and connected in parallel to force fuel from a low pressure source to said high pressure fuel chamber, a timer cylinder having a timer plunger mounted in said pump block and connected to control the supply of fuel from said high pressure fuel chamber to said injection line, a cam shaft for said pump block having spaced cams constructed to reciprocate said pump plungers alternately and with two working strokes each on every complete rotation of said cam shaft, additional means in said pump block for reciprocating said timer plunger, means associated with said timer plunger for regulating the beginning and duration of supply of fuel from said high pressure fuel chamber to said injection line on each cycle, said means being constructed and arranged to close communication between said fuel chamber and said injection line and maintain 'a substantially lower fuel pressure in said injection line during the balance of each cycle, and a com mon control means associated with said pump a low pressure fuel source, an outlet leading to a high pressure fuel storage reservoir, and a spill plungers and responsive to fuel pressure within said high pressure fuel chamber for automatically regulating the quantity of fuel supplied on each working stroke of said pump plungers to maintain a predetermined substantially constant pressure of fuel in the said high pressure fuel chamber.

12. In a fuel pump and timer mechanism of the character described, a pump block, a timer cylinder mounted therein, said parts being formed with an inlet communicating with a high pressure fuel supply, an outlet communicating with an injection line, and a spill port communicating with a return line to a low pressure fuel source, a check valve normally closing communication between said inlet and said outlet, a timer plunger within said cylinder having an axial passage normally providing communication between said outlet and said spill port, a stem on said check valve normally spaced from the adjacent end of said plunger containing the said axial passage when said plunger has completed its working stroke, the adjacent ends of said stem and plunger being formed to provide a valve and valve seat respectively to seal said axial passage on the working stroke of said plunger, and means for reciprocating said plunger to first seal said axial passage and then open said check valve on the working stroke of said plunger.

13. Apparatus according to claim 12, wherein said means for reciprocating the plunger comprises a cam shaft, a cam thereon withrelatively steep sides, and a pivoted lever operatively interconnecting said cam and said plunger for snapaction movement of the latter.

14. Apparatus according to claim 12, wherein said means for reciprocating the plunger comprises a cam shaft, a cam thereon having a rise 7 with relatively steep sides, a lever operatively interconnecting said cam with said plunger, said lever having an arm provided with spaced forks adapted to ride on the circumference of the cam shaft on opposite sides of said cam, a bearing pin between said spaced forks in position to be contacted by said cam rise to provide snap-action movement of said lever and plunger, an eccentric pivot for said lever, and means for adjusting said pivot to alter the beginning and duration of injection.

15. In a. fuel pump of the character described, a pump block, a pump cylinder therein, said parts port communicating with a return line to said low pressure fuel source, a pump'plunger slidably and rotatably mounted within said cylinder, means for reciprocating said plunger to produce working strokes thereof, a check valve between said inlet and said outlet, said parts being constructed and arranged so that said plunger on its working stroke first closes said inlet to trap fuel in said cylinder and then forces trapped fuel under high pressure past said check valve to said outlet, and thence to said high pressure fuel storage reservoir, said plunger also having an ,axial internal passage extending from said trapped fuel chamber and communicating with a helical external groove formed thereon and adapted to register with said spill port during the working stroke of said plunger to terminal fuel supply to said high pressure tration with said spill port, and means responsive to fuel pressure within said high pressure fuel storage reservoir for actuating said rotating means.

16. Apparatus according to claim 15, wherein said means for rotating the pump plunger comprises a rack slidably mounted in the pump block, a gear meshing with said rack and operatively connected with said plunger to rotate the latter upon sliding movement of said rack, a control piston responsive to fuel pressure in said high pressure fuel storage reservoir, and operative interconnections between said control piston and said rack.

17. Apparatus according toclaim 15, wherein the said means for rotating the pump plunger comprises a rack slidably mounted in said block, a gear meshing withsaid rack and operatively interconnected with said plunger to rotate the latter upon slidingmovement of said rack, a control mechanism including a piston of-relatively small cross-sectional area responsive to fuel pressure within said storage reservoir, and an opposed piston of substantially larger cross-sectional area responsive to a substantially constant applied fluid pressure adapted to normally maintain the pistons in equilibrium position, and operative interconnections between said pistons and said rack for producing sliding movement of said rack when said pistons move out of equilibrium po sition.

,18. A unitary fuel pump and timer assembly comprising a pump block and crank case, a cam shaft mounted in said crank case, two spaced fuel pumps mounted in said block in alignment with said cam shaft, each having a cylinder and a reciprocating plunger, connecting passages in said block and pumps constructed and arranged so that said pumps operate in parallel to force fuel from a low pressure source to a high pressure connection adapted to be connected with a reservoir, spaced cams on said cam shaft for reciprocating said pump plungers, said cams being angularly displaced so that said pumps operate alterspaced cams and a pivoted lever mounted in said.

crank case, and means associated with said timer mechanism for controlling the beginning and duration of injection by the reciprocation of said/ timer plunger.

19. A fuel pump for an internal combustion engine operating with fuel injection and having an injection line, comprising a pump cylinder with plunger operating therein for drawing fuel from a low pressure source and supplying it under high pressure to a fuel flow path, a timer cylinder with a timer plunger operating therein and connected for delivery ofhigh pressure fuel I to the engine injection line, a high pressure fuel storage reservoir connected in said fuel flow path intermediate said pump cylinder and said timer cylinder, pressure actuated means responsive to the fuel pressure in said fuel storage reservoir to control the delivery of fuel by said pump plunger to said storage reservoir, 8. pressure release line, and control means associated with said timer cylinder and timer plunger for connecting, and then disconnecting on each cycle, said fuel storage reservoir with said injection line to thereby control the beginning and duration of injection, and for then promptly connecting said injection line with said pressure release line at the termination of injection.

20. A fuel pump for an internal combustion engine operating with fuel injection and having an injection line, comprising pumping means adapted to be driven in synchronism with the engine for drawing fuel from a low pressure source and supplying it under high injection pressure to a fuel flow path, timing means also adapted to .be driven in synchronism with the engine for connecting and then disconnecting said fuel flow path with said injection line to thereby control the beginning and duration of injection on each cycle, a high pressure fuel storage reservoir connected in said fuel flow path intermediate said pumping means and said timing means. pressure responsive means for maintaining a substantially constant high pressure of fuel in said storage reservoir whereby the injection line is supplied with fuel at the substantially constant high injection pressure uninfluenced by surges from" said pumping means during each injection period. and additional means for promptly releasing the pressure in said injection line at the termination of injection on each cycle.

KALMAN J. 'DE JUHASZ.

FREDERICK J. VIILFORTH, JR.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Bremser Aug. 14, 1945 

